ISSN No: 2348-4845
International Journal & Magazine of Engineering,
Technology, Management and Research
A Peer Reviewed Open Access International Journal
The pump is very critical factor for farming in this region and its carpentry level construction without testing and calibration has motivated us to take up this pump for anal-ysis and carry out the optimization. Electricity expenses are provided by Government of Kerala in the form of sub-sidies to farmers.
2. Design Premises:
Main parts of Traditional pumping system include- Dis-charge duct, suction duct, Shaft, Impeller, and Hub.
3. Elements of the system
3.1 Discharge duct (petty)
It is the main part of the system and is used for discharg-ing the water. Usually it is 5 meter in length, 80cm wide and 18cm in height. Wood is the preferable material.
3.2 Suction duct (para):
Para is another main part of Traditional pumping system.
It is used for sucking the water from paddy field. It is a
wooden part, cylindrical in shape, which contains impel-ler and part of the main shaft. It has two parts, upper and lower. The upper part is 1 meter in length and lower part
is 65 cm long, which is always filled with water.
Abstract:
The main objective of this project is to Conserve Energy, without affecting productivity and performance. The case study is about aTraditional and outdated pumping system
used in Paddy field all over the country for irrigation pur
-pose. The efficiency of such pumping systems are lower,
due to poor design. The manufacturer of the pumping
system has not considered its efficiency because the elec
-tricity used is, made free of cost by the government. The PETTY and PARA# is one of the major Traditional Pump-ing system used in Kerala for irrigation purpose. A 100%
modification is not possible as the system is already in
place, rather optimizing the impeller blade to enhance the discharge is a viable solution.The project involves
modi-fication of Traditional Pumping system by re-designing
its impeller.The so modified parts are analyzed using suit
-able software’s such as Ansys to check its credibility.
Keyword:
Petty and Para, Impeller design, CFD simulation, Opti-mization
1.Introduction:
Axial flow pumps are widely used in kuttanad, Alappuzha district in Kerala for dewatering the agricultural field to
render them for farming. Due to typical topography,
inter-mittence dewatering of field are essential for their utiliza
-tion. An axial flow pump (Traditionally known as petty
and Para) has been used for years and the system has gone
minimal modification from time to time.
Adarsh C K
Undergraduate Student, Dept of Mechanical Engineering, Sarabhai Institute of Science and Technology, Trivandrum, India.
Jayaram.V
Assistant Professor,
Dept of Mechanical Engineering, Sarabhai Institute of Science and Technology, Trivandrum, India.
Farooque K
Undergraduate Student, Dept of Mechanical Engineering, Sarabhai Institute of Science and Technology, Trivandrum, India.
Naveen kumar R
Undergraduate Student, Dept of Mechanical Engineering, Sarabhai Institute of Science and Technology, Trivandrum, India.
Mahesh Rajendran
Design Engineer Yanbu Steel Company,
Yanbu, Saudi Arabia.
Jayasankar.V
Design Engineer, Yanbu Steel Company,
Yanbu, Saudi Arabia.
ISSN No: 2348-4845
International Journal & Magazine of Engineering,
Technology, Management and Research
A Peer Reviewed Open Access International Journal
Total head (Manometric head) – un flooded
Hm = Hd+ Hfs + Hfd + Hdl + Hb + Hi+Hfv
Hm= 4.055 m= 13.303 ft
Total head (Manometric head) – flooded
Hm1= Hm– 1
Hm1 = 3.055 m= 10.022 ft
Rated discharge in Gallons per minute Q’ = 15850×Q
Q’ = 15850×0.593 Q’ = 9399.05 gpm
Specific Speed of pump (unfloodedcondition)
For flooded, N=8605.8 rpm,Axial pumps give best per
-formance for specific speeds above 7500 rpm. Specific speeds within the range of 7500 rpm to 15000 rpm are the region where the efficiency obtained is high. Axial pumps
within this range can pump up to a head of 35 feet.In our case, the manometric head lie within 15
feet.Recalculat-ing the new design speed with specific speed as 8000rpm
= =
4.2 Design of pulley[4]
Power of the motor,P = 50HP
Diameter of Driver pulley, D = 200 mm
Thickness of Belt used,Tb =10 mm
3.3 Pulley system:
This Pulley is driven by a motor with a cross belt. The motor pulley is very small as compared to this pump pul-ley so that the speed of pump is considerably reduced. Size of the pulley is 66 cm in diameter. Usually the mate-rial used for making pulley is of cast iron.
3.4 Impeller:
Impeller-Blade[1] is the main and important part of this Traditional pumping system, because its size and shape
determines the efficiency. Usually the number of blades
are limited to 5or 6.
4.Design
4.1 Design of pump[2]
Speed of Pump, N=500 rpm
Rated Discharge, Q=0.593m3/s
Diameter of suction Pipe, Ds=1m
Length of suction Pipe, Ls=1.37m
Darcy Frictional Factor, F=0.00925 Dimensions of Discharge Pipe
L =4.5m, B=0.7m, H=0.14m
Suction head, Hs=0m
Discharge head (Unflooded) Hd=1.18m
Discharge head (flooded) Hd1=0.18m
Diameter of top and bottom of hub
Dm1=0.42m, Dm2=0.22m
The total head of the pump is the sum of suction head, discharge head and all losses in pump, suction pipe, and discharge pipe with other miscellaneous losses.
ISSN No: 2348-4845
International Journal & Magazine of Engineering,
Technology, Management and Research
A Peer Reviewed Open Access International Journal
Stress Analysis[5] shows that the shaft is safe The de-sign of impeller, shaft, belt, pulley and recommendation of bearing is the major part of design. To know whether the design can generate required amount of output power, discharge, we have to analyze of the design
Recommended speed of pump N = 580 rpm
Recommended dimensions of pulley Diameter D = 400 mm Breadth B = 180 mm Rim thickness = 5 mm Hub length = 120 mm
Recommended shaft diameter d = 75 mm
Belt material - canvas
Belt length (cross belt) L = 11.93 m
Recommended bearing-SKF 621
5. Analysis
The project Design is validated through Ansys. The de-sign can’t be declared safe, until it is subjected to suitable simulation.The two types of analysis that was conducted was:
1. CFDanalysis [6] of the pump under variable condi-tions.
2. Static load analysis of the pump shaft using
ANSYS:
For optimization of the pumping system [7], two param
-eters are varied, one is the number of blades and the other
is blade angle [8].To reach the optimum configuration, the
number of blades and vane angle is varied over a range.
The numbers of blades are varied from 3 to 6, i.e. models of 3 vanes, 4 vanes, 5 vane, and 6 vanes are created and for each set of vane, the vane angle is varied from 38 to 46
degrees. So for each impeller having a definite number of
blades, we have a set of 5 impellers having blade angles of 38, 40,42,44,46. Analysis is performed for each set
Speed of Driver (Motor) pulleyNm=960rpm Speed of Driven Pulley,Np=580rpm
Width of Belt used,b =140 mm
Diameter of Driven Pulley D= 400 mm Breadth of Pulley B= 180 mm
No. of arms, i = 6, if D > 450
Thickness of Rim tr= 5 mm Hub Length H=120 mm
Belt Type: Heavy duty/single belt
As per standards,
Similarly all checks are made as per standards and no substantial deviation was found.
4.3 Design of shaft
Diameter of Shaft, d =75 mm (Provided) Shaft Material:
Mild Steel
Weight of hub and bladesW1 =150 kg Weight of shaft, W2 =4.68 Kg
ISSN No: 2348-4845
International Journal & Magazine of Engineering,
Technology, Management and Research
A Peer Reviewed Open Access International Journal
The performance curve is an indication of variation of
ve-locity with blade angles of different configurations. While
analyzing this curve, it observed that the existing 6 blade -42º degree impeller has very less velocity as compared
with other configurations. At the same time results shows a promising number for 4 blade- 44 º configurations.From the second performance curve(blade angle vs. discharge),
an effective correlation between discharge, blade angles and number of blades can be estimated. The ultimate aim is to maximize the discharge. The existing 6 vane 42º im-peller gives a discharge of 3.32 m3/s, while a 4 vane 44º impeller would provide a discharge much higher than that
of 6 vane configuration (12.38 m3/s). In this waya 4 vane 44º impeller seems more efficient than existing impeller.
Performance Curve 2:
Blade Angle Vs. Discharge
From the third performance curve, a picture of blade
an-gle and efficiency can be plotted. The maximum efficien
-cy is 32.54% and the concerned configuration isa 4 vane
44º impeller. The existing model, i.e. 6 vane 42º impeller
has an efficiency of only 8.72%. It is worth noting that a whopping 272% increase in efficiency can be achieved if
one of the key component is replaced.
Performance Curve 3:
Blade Angle Vs. Efficiency
6 blade Vane Impeller
5 blade Vane Impeller
Stream Lines in 6 Vane 42º Impeller
Flow Characteristics Result for 4 Vane 44º
Impeller
ISSN No: 2348-4845
International Journal & Magazine of Engineering,
Technology, Management and Research
A Peer Reviewed Open Access International Journal
Saving in pumping period
From the table it is clear that there is a saving of 6.19
days if the optimized configuration is employed for
clearing 600 acres of plot having 1 m height of water there by saving energy and money.
7. References:
#-The Petty and Para (Local language: Malayalam)is an
old term used because of its shape.
Para (Suction duct)sucks the water from Paddy .Petty (Discharge duct)discharges the water. The minimum
length of Petty is 15 feet. The system needs to be
reas-sembled for any further modification.
1.N. N. Arshenevskii, E. M. Natarius- “Stable opera
-tion of sta-tions with axial-flow pumps” November 1981, Volume 15, Issue 11, Pages 678-683, Power Technology
and Engineering-springer
2.A.J Stepanoff –“Centrifugal and Axial Flow Pumps”-Krieger Publishing company, Revised edition (28 feb 1993)
3. Dr. R.K Bansal –“A Text Book of Fluid Mechanics”, page293 onwards, Laxmi publication -Ninth edition (2010)
4. Faires V.M-“Design of Machine Element” Macmillan,
01-Jun-1965 - Technology & Engineering
5. Mahadhev and Balaveer Reddy -“Design Data Hand Book for Mechanical Engineers : In SI and Metric Units” ( 3rd Edition)CBS Publisher
6. Anderson –“Computational Fluid Dynamics”ch1.
2-The Governing Equations of Fluid Dynamics and Ch2. 5- Grids and Meshes, With Appropriate Transformations -
McGraw Hill Education (India) Private Limited
7. Helmut Jaberg –“Hydraulic aspects in design and operation of axial-flow pumps”-(DESWARE) Institute
for Hydraulic Machinery, Graz, Austria
8.Max J. Miller and James E. Crouse -“Design and over
-all performance of an axial-flow pump rotor with a blade-tip diffusion factor of 0.66”- Lewis Research Centre
CleveZand, Ohio
The above table represents the various efficiencies at
different vane angles and number of vanes during simulation. From the table itself it is very clear that the
existing impeller has very low efficiency as compared to
other types. Because of this reason we have to adopt a
new model of impeller which gives more efficiency. The 4 vane 44º impeller have more efficiency than that of all
other types.
6.Conclusion:
The aim of project is a comparison between various de-sign of impeller with different number of vanes and vane angle. The number of vanes are varied from 3 to 6 and vane angles from 38 to 46 in steps of 2.
Proposed Design:
The simulation results concluded that 4 vane impeller with 44° vane angle gives maximum discharge for same power input hence performance of pump is optimized with this
configuration of impeller .The new configuration of im
-peller can be recommended to manufacturer. In order to compensate the huge amount of impeller losses, suitable
modification in the vane shape is appropriate. The weight
